JP3105405B2 - Vertical crusher - Google Patents
Vertical crusherInfo
- Publication number
- JP3105405B2 JP3105405B2 JP06228215A JP22821594A JP3105405B2 JP 3105405 B2 JP3105405 B2 JP 3105405B2 JP 06228215 A JP06228215 A JP 06228215A JP 22821594 A JP22821594 A JP 22821594A JP 3105405 B2 JP3105405 B2 JP 3105405B2
- Authority
- JP
- Japan
- Prior art keywords
- rotary table
- vertical
- speed reducer
- bearing
- disposed
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Crushing And Grinding (AREA)
Description
【0001】[0001]
【産業上の利用分野】本発明は、回転テーブルと粉砕ロ
ーラとの協働により、セメント原料、スラグ、クリンカ
やセラミックス、化学品などの原料を粉砕する竪型粉砕
機に係り、特に回転テーブルに負荷される鉛直荷重は回
転テーブルに回転力を付与する減速機でなく別個に回転
テーブル外周部下方に設置した静圧軸受に支承させ、減
速機の小型化を図り減速機の振動トラブルを防止し、か
つ、静圧軸受部の熱変形を配慮した竪型粉砕機に関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vertical grinding machine for grinding raw materials such as cement raw materials, slag, clinker, ceramics, and chemicals by cooperation of a rotary table and a grinding roller. The vertical load applied is not supported by the reducer that applies rotational force to the rotary table, but is supported by a hydrostatic bearing that is separately installed below the outer periphery of the rotary table, reducing the size of the reducer and preventing vibration problems of the reducer. The present invention also relates to a vertical pulverizer that considers thermal deformation of a hydrostatic bearing.
【0002】[0002]
【従来の技術】石灰石やスラグ、セメント原料などの原
料を細かく粉砕し粉体とする粉砕機の一種として、図1
0に示すように、回転テーブルと粉砕ローラとを備えた
竪型粉砕機1が広く用いられている。この種の粉砕機
は、円筒状ケーシング15の下部において電動機2Bに
より減速機2を介して駆動されて低速回転する円盤状の
回転テーブル3Aと、その上面外周部を円周方向へ等分
する箇所に油圧などで圧接されて従動回転する複数個の
粉砕ローラ4とを備えている。2. Description of the Related Art As one type of a crusher for finely pulverizing raw materials such as limestone, slag and cement raw material into powder, FIG.
As shown in FIG. 1, a vertical pulverizer 1 having a rotary table and a pulverizing roller is widely used. A pulverizer of this type includes a disk-shaped rotary table 3A that is driven by an electric motor 2B via a speed reducer 2 and rotates at a low speed at a lower portion of a cylindrical casing 15 and a portion that equally divides an outer peripheral portion of an upper surface thereof in a circumferential direction. And a plurality of crushing rollers 4 which are pressed by hydraulic pressure or the like and driven to rotate.
【0003】粉砕ローラ4はケーシング15に軸6によ
って揺動自在に軸支されたアーム5とアーム7A、7B
を介して油圧シリンダ9のピストンロッド10に連結さ
れており、油圧シリンダ9を作動させることにより、粉
砕ローラ4を回転テーブル3A上に押圧して原料への粉
砕圧力を与えている。3Sは回転テーブル3Aの外周縁
に設けられ原料層厚を調整するダムリング、14は回転
テーブル3Aをオーバフローした粉砕産物の環状空間通
路、17は原料投入シュート、18は環状空間通路14
に落下した粉砕産物を掻き寄せるスクレーパである。ス
クレーパ18で掻き寄せられた粉砕産物は、図10に示
すように、排出シュート19を介して機外へ排出され
る。The crushing roller 4 includes an arm 5 pivotally supported on a casing 15 by a shaft 6 and arms 7A and 7B.
Is connected to the piston rod 10 of the hydraulic cylinder 9 via the hydraulic cylinder 9. By operating the hydraulic cylinder 9, the crushing roller 4 is pressed onto the rotary table 3 </ b> A to apply crushing pressure to the raw material. 3S is a dam ring provided on the outer peripheral edge of the rotary table 3A to adjust the thickness of the raw material layer, 14 is an annular space passage for the pulverized product overflowing the rotary table 3A, 17 is a material charging chute, and 18 is an annular space passage 14
A scraper that scrapes the crushed product that has fallen into The crushed product scraped by the scraper 18 is discharged out of the machine through a discharge chute 19 as shown in FIG.
【0004】このような竪型粉砕機において、回転テー
ブルの中央部へ原料投入シュート17で供給された原料
は、回転テーブル3Aの回転によりテーブル半径方向の
遠心力を受けて回転テーブル3A上を滑る時に回転テー
ブル3Aにより回転方向の力を受け、回転テーブル3A
との間で滑って回転テーブル3Aの回転数よりいくらか
遅い回転を行う。以上2つの力、すなわち、半径方向と
回転方向の力とが合成され、原料は回転テーブル3A上
を渦巻状の軌跡を描いて回転テーブル3Aの外周部へ移
動する。この外周部には、ローラが圧接されて回転して
いるので、渦巻線を描いた原料は粉砕ローラ4と回転テ
ーブル3Aとの間へローラ軸方向とある角度をなす方向
から進入して噛込まれて粉砕される。In such a vertical pulverizer, the raw material supplied to the center of the rotary table by the raw material charging chute 17 receives the centrifugal force in the table radial direction by the rotation of the rotary table 3A and slides on the rotary table 3A. Sometimes, a force in the rotating direction is received by the rotating table 3A, and the rotating table 3A
And a rotation somewhat slower than the rotation speed of the turntable 3A is performed. The above two forces, that is, the force in the radial direction and the force in the rotation direction are combined, and the raw material moves on the turntable 3A to the outer periphery of the turntable 3A along a spiral trajectory. Since a roller is pressed against this outer peripheral portion and is rotating, the raw material describing the spiral enters the crushing roller 4 and the rotary table 3A from a direction forming an angle with the roller axis direction and bites. Rarely crushed.
【0005】一方、回転テーブル3Aの直下に配設され
た減速機2では、頂部に突出した出力軸に取り付けた水
平円板に回転テーブル3Aが載置され連結されており、
減速機は回転テーブル3Aを介して伝達される全荷重を
負荷させながら回転テーブル3Aに横型の電動機2Bに
より付与された回転力を与えるようになっている。On the other hand, in the speed reducer 2 disposed immediately below the rotary table 3A, the rotary table 3A is mounted on and connected to a horizontal disk attached to an output shaft projecting from the top.
The speed reducer applies a rotational force applied by the horizontal electric motor 2B to the rotary table 3A while applying the full load transmitted through the rotary table 3A.
【0006】[0006]
【発明が解決しようとする課題】上に述べたように、従
来の竪型粉砕機1は、回転テーブル3Aが回転テーブル
3Aの直下に同芯状に配設した減速機2の出力軸に直結
され、回転テーブル3Aや粉砕ローラ4の自重ばかりで
なく、油圧シリンダ9に付勢された粉砕力をも常時減速
機2が支承することになり、このため、減速機2は非常
に大きな剛性を保持する必要があり、サイズの大型化に
よるコストアップの要因となっていた。そのうえ、粉砕
時の変動荷重に起因する振動が常時伝達され、減速機内
部の歯車を始めとする動力伝達部に損傷を与える原因と
なり、減速機トラブルの発生による寿命の低下やメンテ
ナンスに多大の費用と労力の消費を余儀なくさせられて
いた。また、減速機2そのものも電動機2Bの水平な出
力軸を竪軸に変換するベベル減速機構を下部に内蔵する
ため、減速機2の高さや占有面積(設置スペース)が大
きくなり、コスト高を招くとともに、大きな建屋面積を
必要としていた。また、例えば、高温クリンカ(常温8
0℃〜150℃、最大200℃)などの高温原料に粉砕
熱が加わって、回転テーブルは温度上昇し、そのため回
転テーブルはお碗を伏せたような熱変形をするために、
静圧軸受30aは摺動面が片当りして偏心荷重を受け損
傷を受けたり寿命を短くするなどの問題が生じていた。As described above, in the conventional vertical crusher 1, the rotary table 3A is directly connected to the output shaft of the speed reducer 2 which is disposed concentrically directly below the rotary table 3A. The reduction gear 2 always supports not only the weight of the rotary table 3A and the crushing roller 4 but also the crushing force urged by the hydraulic cylinder 9, so that the reduction gear 2 has a very large rigidity. It is necessary to maintain the size, which has caused a cost increase due to an increase in size. In addition, vibration caused by the fluctuating load during grinding is constantly transmitted, causing damage to the power transmission unit including the gears inside the reduction gear, resulting in a reduction in life due to the occurrence of a reduction gear trouble and a large cost for maintenance. And was forced to consume labor. In addition, since the reduction gear 2 itself has a built-in bevel reduction mechanism for converting the horizontal output shaft of the electric motor 2B into a vertical axis, the height and the occupied area (installation space) of the reduction gear 2 are increased, resulting in an increase in cost. At the same time, a large building area was required. Also, for example, a high-temperature clinker (normal temperature 8)
(0 ° C to 150 ° C, maximum 200 ° C), the heat of crushing is applied to the high-temperature raw material, and the temperature of the rotary table rises.
The hydrostatic bearing 30a has a problem in that the sliding surface receives an eccentric load due to a one-sided contact and is damaged or shortened in life.
【0007】[0007]
【課題を解決するための手段】以上のような課題を解決
して、トラブルフリーな動力伝達機構を備えた竪型粉砕
機とし、かつ、省スペースと設備費を低減するため、本
発明では、回転テーブルの外周部上面に複数個の回転自
在な粉砕ローラを配設し、回転テーブル上に供給された
原料を粉砕ローラに所定の圧力を与えて回転テーブル上
面と粉砕ローラ周面との間で粉砕する竪型粉砕機におい
て、該回転テーブルに回転力を付与する減速機を該回転
テーブル直下の中央部に配設するとともに、該回転テー
ブルに負荷される自重ならびに粉砕力などの鉛直荷重を
支承する静圧軸受を該回転テーブル外周部の粉砕ローラ
押圧領域の直下に配設し、該静圧軸受を支承する柱脚を
該減速機とは別体に設け、該静圧軸受は前記柱脚の上面
との間に球状ピボットを介して押圧されるセンタピボッ
トタイプの軸受とするとともに、該静圧軸受の側面には
水平方向の移動を抑止する側面押えを配設し、かつ、該
回転テーブルは粉砕ローラが載置される平板部と該平板
部の外周下方へ延在し前記静圧軸受に下端が支承されあ
る程度の高さを保有し肉厚を薄くした外周円筒部と該平
板部の中心部下方へ延在し前記減速機の出力軸と下端が
係合される内周円筒部を有する形状とし、該回転テーブ
ルに負荷される鉛直荷重が該外周円筒部をほぼ垂直に伝
わって該静圧軸受で支承される構成にし、該内周円筒部
を、該内周円筒部の下端に一体的に取付けた回転筒、及
び、該回転筒の外周囲に内周面が摺動可能とされて嵌装
された支持環を介して、支持するためのステーを該柱脚
との間に円周複数本設けた構成にした。また、第2の発
明では、減速機を竪型二段遊星減速機とし、第3の発明
では、さらに減速機の直下にピットを形成して該減速機
を回転駆動する竪型電動機を該ピット内に配設した。SUMMARY OF THE INVENTION In order to solve the above-mentioned problems and to provide a vertical crusher having a trouble-free power transmission mechanism, and to save space and equipment costs, the present invention provides: A plurality of rotatable crushing rollers are arranged on the outer peripheral surface of the rotary table, and a predetermined pressure is applied to the raw material supplied on the rotary table to apply a predetermined pressure to the crushing roller. In a vertical pulverizer for pulverizing, a speed reducer for applying a rotational force to the rotary table is disposed at a central portion immediately below the rotary table, and supports a vertical load such as its own weight and a pulverizing force applied to the rotary table. A static pressure bearing is provided immediately below the grinding roller pressing area on the outer periphery of the rotary table, and a column base for supporting the static pressure bearing is provided separately from the speed reducer. Spherical pivot between top of A center pivot type bearing that is pressed through a bearing, a side press that suppresses horizontal movement is disposed on the side of the hydrostatic bearing, and a crushing roller is mounted on the rotary table. is the flat plate portion and the static pressure bearing is lower in a bearing extending to the outer periphery below the flat plate portion that Oh
An outer cylindrical portion having a certain height and a reduced thickness, and having an inner cylindrical portion extending below the center of the flat plate portion and engaging the output shaft and the lower end of the speed reducer, a configuration in which the vertical load applied to the rotary table is supported by the static pressure bearings transmitted substantially perpendicular to the outer peripheral cylindrical portion, the inner peripheral cylindrical portion
A rotating cylinder integrally attached to a lower end of the inner peripheral cylindrical portion, and
And the inner peripheral surface is slidably fitted around the outer periphery of the rotary cylinder.
A support for supporting the pedestal through the support ring
And a plurality of circumferences are provided between them. In the second invention, the speed reducer is a vertical two-stage planetary speed reducer, and in the third invention, a pit is further formed immediately below the speed reducer, and the vertical electric motor for rotating and driving the speed reducer is provided in the pit. It was arranged inside.
【0008】[0008]
【作用】本発明においては、回転テーブルに負荷される
鉛直荷重を支承する静圧軸受を回転テーブルの外周部下
端に配設し、回転テーブルの自重や回転テーブル外周で
粉砕テーブルによって押圧された粉砕力などの鉛直荷重
は外周円筒部をほぼ垂直に伝わって静圧軸受で支承さ
れ、一方回転力は減速機の出力軸に係合された内周円筒
部によって回転テーブルへ伝達される。したがって、回
転テーブルの鉛直荷重による変形が少なく、かつ、平板
部に与えられる高温原料や粉砕熱による熱伝達による内
周円筒部下端や外周円筒部下端の熱歪も従来構造の竪型
粉砕機などに採用される略平板状の回転テーブルに比べ
て極めて小さいので、静圧軸受や減速機に負荷変形なら
びに熱歪による悪影響が少なく、機器の損傷の低減と長
寿命化が図られる。また、静圧軸受は上下方向と水平方
向の移動は拘束されるが、傾動は拘束されずに自由とさ
れるので、運転中の回転テーブルの微小傾動に追従し、
静圧軸受に無理な力がかからず損傷が防止される。さら
に、第2の発明では、従来構造のベベル減速機に代えて
遊星二段減速機を採用するので減速機の小型化が図ら
れ、第3の発明では、減速機の直下にピットを設けて竪
型電動機を収納し、減速機と直結することで、ミル自体
が小型となり、工場の省スペース化を実現するばかりで
なく、竪型粉砕機全体の設備費の低減が達成される。According to the present invention, a hydrostatic bearing for supporting the vertical load applied to the rotary table is provided at the lower end of the outer peripheral portion of the rotary table, and the weight of the rotary table and the pulverization pressed by the pulverizing table at the outer periphery of the rotary table. A vertical load such as a force is transmitted almost vertically through the outer cylindrical portion and supported by a hydrostatic bearing, while the rotational force is transmitted to the rotary table by the inner cylindrical portion engaged with the output shaft of the speed reducer. Therefore, the deformation of the rotary table due to the vertical load is small, and the thermal distortion of the lower end of the inner cylindrical portion and the lower end of the outer cylindrical portion due to the heat transfer by the high-temperature raw material or the crushing heat given to the flat plate portion also has the conventional structure of a vertical pulverizer. Since the size of the rotary table is extremely small as compared with the substantially flat rotary table used in the above, the adverse effects due to load deformation and thermal strain on the hydrostatic bearing and the reducer are small, and the damage to the equipment and the service life can be reduced. In addition, although the movement of the hydrostatic bearing in the vertical and horizontal directions is constrained, the tilting is free without being constrained, so it follows the slight tilt of the rotating table during operation,
Unreasonable force is not applied to the hydrostatic bearing to prevent damage. Furthermore, in the second invention, a planetary two-stage speed reducer is used instead of the conventional bevel speed reducer, so that the size of the speed reducer is reduced. In the third invention, a pit is provided immediately below the speed reducer. By storing the vertical motor and connecting it directly to the speed reducer, the mill itself can be reduced in size, not only to save space in the factory, but also to reduce the equipment cost of the entire vertical mill.
【0009】[0009]
【実施例】以下図面に基づいて本発明の実施例の詳細に
ついて説明する。図1〜図6は本発明の実施例に係り、
図1は竪型粉砕機の全体縦断面図、図2は図1のA−A
視の断面平面図、図3は竪型粉砕機の要部拡大縦断面
図、図4は静圧軸受部の要部拡大縦断面図、図5は減速
機(竪型二段遊星減速機)の縦断面図、図6は減速機
(遊星減速機)の説明図である。また、図7〜図9は回
転テーブルの熱変形解析図である。図1〜図3に示すよ
うに、本発明の竪型粉砕機1においては、竪型粉砕機1
を設置する中心軸直下にピット100を穿設するととも
に、下方より上方に向かって順次竪型電動機からなる電
動機2B、竪型二段遊星減速機からなる減速機2および
竪型粉砕機1が配設される。竪型粉砕機1は、直立円筒
状のケーシング15の内部にケーシング15と同軸状に
回転テーブル3Aが竪軸回りに回転自在に配設され、回
転テーブル3Aの外周部直上には複数個(図1〜図3の
実施例では4個)の粉砕ローラ4が載置され、二重円筒
で形成される柱脚30の頂上に設置される軸受6Aの回
転軸6回りに揺動自在なアーム5およびアーム7A、7
Bを介して油圧シリンダ9により回転テーブル3A上に
押圧され、従動される。回転テーブル3Aの形状は、図
に示すように、縦断面が上部の水平な平板部3Xと平板
部3Xの外周下方へ接続する略円筒形状の外周円筒部3
Yと平板部3Xの中心部透孔の周りの下方へ接続する円
筒形状の内周円筒部3Zとが一体となった構造とされ
る。回転テーブル3Aの形状を上述のような形状にした
理由について述べる。本出願人は、高温原料、例えば、
常用80℃〜150℃、最大200℃のクリンカを粉砕
する場合における回転テーブルの熱変形について、実操
業状態の負荷条件と温度条件を考慮して有限要素法(N
ASTRAN)による解析を試みた。回転テーブル3A
について、10数種類のタイプについて、それぞれ同じ
境界条件を与えてその熱変形状態を観察すると、形状に
よって熱変形に大きな差異があることが判明した。ここ
では、従来タイプのシンプルな平板状の回転テーブル3
A(TYPE A)と最も熱変形の少ない回転テーブル
3A(TYPE B)および熱変形が中間程度の回転テ
ーブル3A(TYPE C)の解析結果を示す。図7〜
図9は、各々TYPE A、TYPE B、TYPE
Cの回転テーブル3Aの解析結果を示したもので、その
結果は、静圧軸受30a近傍の熱歪がTYPE Aでは
1100μmもあったものが、TYPE Bでは300
μmに激減した(TYPE Cでは約600μm)。以
上の結果より判断すると、従来構造の平板状のTYPE
Aでなく、平板部3Xにそれぞれ外周円筒部3Yと内
周円筒部3Zが接続し、ある程度の高さを保有した形状
の回転テーブル3A(本発明)が熱影響を排除する観点
から望ましいことがわかった。また、TYPE Bにお
いては外周円筒部3Yの肉厚を剛性の許す範囲でかなり
薄くしても熱歪を小さく保つことができることがわかっ
たので、重量軽減によるコストダウンを図ることができ
る。このように、本発明における竪型粉砕機1において
は、従来構造のように減速機2に鉛直荷重を与えること
なく、遊星減速機2とは別途に回転テーブル3Aの自重
や油圧シリンダ9によって付与される粉砕力などの鉛直
荷重を支持する機構としている。したがって、遊星減速
機2は回転駆動のための回転トルクの伝達だけの機能が
あればよく、それだけ小型化できるとともに、粉砕仕事
中の負荷変動に伴う振動現象の影響を受けることが少な
く、振動トラブルによる損傷が軽減され長寿命が達成さ
れる。また、回転テーブルの形状を熱変形の小さいもの
に形成したので、後述する静圧軸受や減速機の熱影響に
よるトラブルが防止される。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The embodiments of the present invention will be described below in detail with reference to the drawings. 1 to 6 relate to an embodiment of the present invention,
FIG. 1 is an overall vertical sectional view of a vertical pulverizer, and FIG.
FIG. 3 is an enlarged vertical sectional view of an essential part of a vertical crusher, FIG. 4 is an enlarged longitudinal sectional view of an essential part of a hydrostatic bearing, and FIG. 5 is a speed reducer (vertical two-stage planetary speed reducer). FIG. 6 is an explanatory view of a speed reducer (planetary speed reducer). 7 to 9 are thermal deformation analysis diagrams of the rotary table. As shown in FIGS. 1 to 3, in the vertical pulverizer 1 of the present invention,
A pit 100 is formed directly below the center axis where the motor is installed, and an electric motor 2B composed of a vertical electric motor, a speed reducer 2 composed of a vertical two-stage planetary reducer, and a vertical pulverizer 1 are sequentially arranged from below to above. Is established. In the vertical pulverizer 1, a rotary table 3A is rotatably disposed around a vertical axis coaxially with the casing 15 inside a vertical cylindrical casing 15, and a plurality of rotary tables 3 (see FIG. 1 to 4 in the embodiment of FIG. 3), and an arm 5 swingable about a rotation axis 6 of a bearing 6A installed on the top of a column base 30 formed of a double cylinder. And arms 7A, 7
The rotary table 3A is pressed by the hydraulic cylinder 9 via B and is driven. As shown in the figure, the shape of the turntable 3A is a horizontal flat plate portion 3X having a vertical cross section and a substantially cylindrical outer circumferential cylindrical portion 3 connected to the lower part of the outer periphery of the flat plate portion 3X.
Y and a cylindrical inner peripheral cylindrical portion 3 </ b> Z connected downward around the central through hole of the flat plate portion 3 </ b> X are integrally structured. The reason why the shape of the turntable 3A is formed as described above will be described. Applicants have identified high temperature raw materials, such as
Regarding the thermal deformation of the rotary table when pulverizing a clinker at a common use temperature of 80 ° C. to 150 ° C. and a maximum of 200 ° C., the finite element method (N
(ASTRAN). Rotary table 3A
When the same boundary condition was applied to each of the dozens of types and the state of thermal deformation was observed, it was found that there was a large difference in thermal deformation depending on the shape. Here, a conventional flat plate-shaped rotary table 3
The analysis results of A (TYPE A), the turntable 3A (TYPE B) with the least thermal deformation, and the turntable 3A (TYPE C) with an intermediate degree of thermal deformation are shown. FIG.
FIG. 9 shows TYPE A, TYPE B, and TYPE, respectively.
C shows the analysis results of the rotary table 3A. The results show that the thermal strain near the hydrostatic bearing 30a was 1100 μm in TYPE A, but 300 mm in TYPE B.
μm (about 600 μm for TYPE C). Judging from the above results, the flat TYPE of the conventional structure
A, the outer cylindrical portion 3Y and the inner cylindrical portion 3Z are connected to the flat plate portion 3X, respectively, and the rotary table 3A (the present invention) having a shape having a certain height is desirable from the viewpoint of eliminating thermal effects. all right. Further, in TYPE B, it has been found that the thermal distortion can be kept small even if the thickness of the outer peripheral cylindrical portion 3Y is considerably reduced as far as the rigidity allows, so that the cost can be reduced by reducing the weight. As described above, in the vertical pulverizer 1 of the present invention, the vertical load is not applied to the speed reducer 2 as in the conventional structure, but is applied by the own weight of the rotary table 3A or the hydraulic cylinder 9 separately from the planetary speed reducer 2. The mechanism supports vertical loads such as crushing force. Therefore, the planetary speed reducer 2 only needs to have a function of transmitting the rotational torque for the rotary drive, and can be downsized accordingly, and is less affected by the vibration phenomenon caused by the load fluctuation during the grinding work. Damage is reduced and a long life is achieved. Further, since the rotary table is formed to have a small thermal deformation, troubles due to the thermal influence of a static pressure bearing and a speed reducer to be described later are prevented.
【0010】回転テーブル3Aの外周部下側にはドーナ
ツ円板状のフランジシュー3Bが固設されるとともに、
該フランジシュー3Bは、図4に示すように、スタンド
40の下方内側に配設された柱脚30の頂部の支持板3
0P上に載置された静圧軸受(スラストパッド)30a
上に積載され、該静圧軸受30aは回転テーブル3Aに
負荷される自重ならびに粉砕力などの鉛直荷重を支承す
る。スラストパッド30aは静圧軸受の一種であり、図
4に示すように、フランジシュー3Bと上面が当接し、
上面に軸受メタル32を貼設したベースメタル31の下
方中央に、下面が球状の球状ピボット35を嵌装したも
のであり、ベースメタル31の側方には、支持板30P
に立設され頂部に湾曲面を有するこけし状の左右一対の
側面押え30Cで押圧され、水平横移動を拘束されるよ
うになっている。このように静圧軸受としてのスラスト
パッド30aは、軸受メタル32、球状ピボット34を
嵌装したベースメタル31で構成される。支持板30P
の中央上部には、球状ピボット35の球面と当接する高
硬度の支持柱30Qが嵌め込まれている。フランジシュ
ー3Bの下面とスラストパッド30aの軸受メタル32
上面は回転テーブル3A回転時の摺動面となり、ベース
メタル31に穿設した潤滑給油口33および給油路33
aを介して潤滑給油される。以上のように構成された静
圧軸受(スラストパッド)30aは、回転テーブル3A
より負荷される自重ならびに粉砕力(粉砕ローラ押圧
力)などの鉛直荷重を支承し、柱脚30を通じて基礎に
伝達するとともに、各粉砕ローラ4に働く刻々変化する
押圧力に起因して生じる回転テーブル3Aの微小傾動
に、球状ピボット35ならびに支持柱30Qの当接位置
が変化追従して摺動面(フランジシュー3B下面および
軸受メタル32上面)に無理な力が負荷されるのを防止
する。スラストパッド30aは、回転テーブル3A上に
積載される複数個(図1〜図4の実施例では4個)の粉
砕ローラ4の直下に、粉砕ローラ1個当り3つが配置さ
れる。また、図3に示すように、回転テーブル3Aの内
周円筒部3Zの下側には頂部にフランジを有する円筒状
の回転筒3Cが回転テーブル3Aと一体的に突設され、
柱脚30より斜め上方内側に延在する円周複数本のステ
ー30Aによって支持された円筒状の固定リング30B
の中に固設された支持環30bに嵌装され、回転筒3C
と支持環30bの間の摺動面は、スラストパッド30a
上面と同様に潤滑給油される。これら2つの摺動面を形
成するスラストパッド30a上面と支持環30b内面の
役割は、スラストパッド30a上面が主として鉛直荷重
を支持するのに対して、支持環30b内面は回転テーブ
ル3Aに負荷される偏心荷重により回転テーブル3Aが
傾斜したり、あるいは水平移動するのを防止し、鉛直荷
重を円周均等化することである。なお、スラストパッド
30aはドーナツ円板状に形成してもよいが、通常は前
述したように各粉砕ローラ4の直下に局部的に配設する
ようにしている。スラストパッド30aは、静圧軸受と
も呼ばれ、軸受メタル32は支持環30b内面と同様に
その材質はホワイトメタル(WJ2)やりん青銅、鉛青
銅、カドミウム合金などを採用し得る。なお、上述の球
状ピボット35や支持柱30Qを有するタイプの静圧軸
受30aの代りに、図4に二点鎖線(仮想線)したよう
に、回転テーブル3Aの下端外周部に楔形状のスリット
50を形成しておくこともでき、静圧軸受(スラストパ
ッド)30aは、回転テーブル3Aより負荷される自重
ならびに粉砕力(粉砕ローラ押圧力)などの鉛直荷重を
支承し、柱脚30を通じて基礎に伝達するとともに、高
温原料の粉砕時や大きな粉砕熱を受けて回転テーブル3
Aが碗状変形しても、回転テーブル3Aの外周部下端に
設けた楔形状のスリット50がこの変形を吸収して熱変
形に起因する片当りを防止し、静圧軸受を保護する。ス
リット50は回転テーブル3Aでなく、フランジシュー
3Bの上面外周部に設けても同一の作用効果を果たすこ
とができる。スリット50を設ける場合の、スリット5
0の寸法はスリット長さ200mm(水平距離)に対し
てスリット最大高さを0.6mmとする。A donut disk-shaped flange shoe 3B is fixed below the outer peripheral portion of the turntable 3A.
As shown in FIG. 4, the flange shoe 3 </ b> B is provided on a support plate 3 at a top of a column base 30 disposed inside a lower part of a stand 40.
Hydrostatic bearing (thrust pad) 30a mounted on the top
The hydrostatic bearing 30a is mounted on the rotating table 3A, and supports a vertical load such as its own weight and a crushing force applied to the rotary table 3A. The thrust pad 30a is a kind of a hydrostatic bearing, and as shown in FIG.
A spherical pivot 35 having a spherical lower surface is fitted in the lower center of the base metal 31 having the bearing metal 32 attached to the upper surface, and a support plate 30P is provided beside the base metal 31.
And is pressed by a pair of left and right side holders 30C in the shape of a kokeshi having a curved surface at the top, thereby restricting horizontal and horizontal movement. Thus, the thrust pad 30a as a hydrostatic bearing is constituted by the bearing metal 32 and the base metal 31 on which the spherical pivot 34 is fitted. Support plate 30P
A high-hardness support column 30 </ b> Q that is in contact with the spherical surface of the spherical pivot 35 is fitted into the upper center of the. Lower surface of flange shoe 3B and bearing metal 32 of thrust pad 30a
The upper surface serves as a sliding surface when rotating the rotary table 3A, and includes a lubricating oil supply port 33 and an oil supply path 33 formed in the base metal 31.
The oil is lubricated through a. The hydrostatic bearing (thrust pad) 30a configured as described above is mounted on the rotary table 3A.
A rotary table that supports a vertical load such as its own weight and a crushing force (crushing roller pressing force) that is transmitted to the foundation through the column base 30 and that is generated due to the constantly changing pressing force acting on each of the crushing rollers 4. The contact position of the spherical pivot 35 and the support column 30Q changes and follows the minute tilt of 3A, thereby preventing an excessive force from being applied to the sliding surface (the lower surface of the flange shoe 3B and the upper surface of the bearing metal 32). Three thrust pads 30a are arranged immediately below a plurality of (four in the embodiment of FIGS. 1 to 4) pulverizing rollers 4 stacked on the rotary table 3A. As shown in FIG. 3, a cylindrical rotary cylinder 3C having a flange at the top is integrally formed with the rotary table 3A so as to protrude below the inner cylindrical portion 3Z of the rotary table 3A.
A cylindrical fixing ring 30B supported by a plurality of circumferential stays 30A extending diagonally upward and inward from the column base 30
The rotary cylinder 3C is fitted on a support ring 30b fixed inside the rotary cylinder 3C.
The sliding surface between the support ring 30b and the thrust pad 30a
It is lubricated and lubricated like the upper surface. The roles of the upper surface of the thrust pad 30a and the inner surface of the support ring 30b forming these two sliding surfaces are such that the upper surface of the thrust pad 30a mainly supports a vertical load, whereas the inner surface of the support ring 30b is loaded on the rotary table 3A. The purpose is to prevent the rotary table 3A from tilting or moving horizontally due to the eccentric load, and to equalize the vertical load around the circumference. The thrust pad 30a may be formed in the shape of a donut disk, but is usually locally disposed immediately below each grinding roller 4 as described above. The thrust pad 30a is also called a hydrostatic bearing, and the material of the bearing metal 32 can be white metal (WJ2), phosphor bronze, lead bronze, cadmium alloy, or the like, like the inner surface of the support ring 30b. In place of the above-described hydrostatic bearing 30a having the spherical pivot 35 and the support column 30Q, a wedge-shaped slit 50 is formed on the outer periphery of the lower end of the rotary table 3A as shown by a two-dot chain line (virtual line) in FIG. The hydrostatic bearing (thrust pad) 30a supports a vertical load such as its own weight and a crushing force (crushing roller pressing force) applied from the rotary table 3A, and is formed on the foundation through the column base 30. In addition to transmitting the heat, the rotary table 3
Even if A is bowl-shaped, the wedge-shaped slit 50 provided at the lower end of the outer peripheral portion of the rotary table 3A absorbs this deformation and prevents a one-sided contact caused by thermal deformation, thereby protecting the hydrostatic bearing. The same operation and effect can be achieved by providing the slit 50 not on the rotary table 3A but on the outer peripheral portion of the upper surface of the flange shoe 3B. When the slit 50 is provided, the slit 5
For the dimension of 0, the maximum slit height is 0.6 mm for a slit length of 200 mm (horizontal distance).
【0011】[0011]
【0012】一方、回転テーブル3Aの回転駆動は、回
転テーブル3Aの中心直下に配設した減速機(本実施例
では竪型二段遊星減速機)2の出力軸2aの頂部外周に
螺設した平歯車と回転筒3Cの内周面に取り付けた内歯
歯車との噛合により実施され、減速機2には回転テーブ
ル3Aに負荷される鉛直荷重が伝達されることはない。
以上のように構成された本発明の竪型粉砕機1では、回
転テーブル3Aは電動機2B、減速機2を介して回転駆
動され、原料は原料投入シュート17および分岐管17
Aを経由して各粉砕ローラ4の直前に落下され、回転テ
ーブル3Aと粉砕ローラ4との間で粉砕され、回転テー
ブル3Aをオーバフローして環状空間通路14へ落下
し、スクレーパ18によって掻き寄せられ原料排出口よ
り機外へ排出される。なお、分岐管17Aはクリンカな
ど摩耗性の強い原料に対する摩耗防止のため、下半分に
堰板17Bを複数個配設して原料を貯め、マテリアル・
クッションを形成する。On the other hand, the rotary drive of the rotary table 3A is screwed around the top outer periphery of the output shaft 2a of a speed reducer (vertical two-stage planetary speed reducer in this embodiment) 2 disposed directly below the center of the rotary table 3A. This is implemented by meshing between the spur gear and the internal gear mounted on the inner peripheral surface of the rotary cylinder 3C, and the vertical load applied to the rotary table 3A is not transmitted to the speed reducer 2.
In the vertical pulverizer 1 of the present invention configured as described above, the turntable 3A is driven to rotate via the electric motor 2B and the speed reducer 2, and the raw material is supplied to the raw material charging chute 17 and the branch pipe 17.
A, falls immediately before each grinding roller 4, is ground between the rotary table 3 A and the grinding roller 4, overflows the rotary table 3 A, falls into the annular space passage 14, and is scraped by the scraper 18. It is discharged outside the machine from the raw material discharge port. The branch pipe 17A is provided with a plurality of weir plates 17B in the lower half to store the raw material so as to prevent abrasion of the raw material having high abrasion such as clinker.
Form a cushion.
【0013】次に、減速機2の詳細について、図5〜図
6に基づいて説明する。本発明で採用される減速機2は
竪型二段遊星減速機であり、減速機2内に上下2段の遊
星部が配設される。下段の遊星部は第1段遊星部と呼ば
れ、第1段太陽歯車S1 と第1段内歯歯車(リングギ
ア)R1 との間に3個の第1段遊星歯車P1 が噛合さ
れ、上段の遊星部は第2段遊星部と呼ばれ、第2段太陽
歯車S2 と第2段内歯歯車(リングギア)R2 との間に
5個の第2段遊星歯車P2 が噛合される。遊星歯車にお
ける減速比iと遊星歯車の個数との間には相関関係があ
り、図6に示すように、減速比iは、内歯歯車(リング
ギア)Rのピッチ円直径dRと太陽歯車Sのピッチ円直
径dSとの比に1を加えた数となるから、一般にピッチ
円直径dRがピッチ円直径dSより大きくなると減速比
iは増大するが、逆に太陽歯車Sと内歯歯車Rとの間に
収納できる遊星歯車Pの個数は減少する。一方、遊星歯
車の個数が多いほど、各々の遊星歯車への動力伝達力の
分担が小さくなり、かつ、太陽歯車Sの直径dSに比べ
て内歯歯車(リングギア)Rの直径dRを相対的に小さ
くできるから減速機2はコンパクトなものになる。Next, details of the speed reducer 2 will be described with reference to FIGS. The speed reducer 2 employed in the present invention is a vertical two-stage planetary speed reducer, in which two upper and lower planetary portions are disposed. The lower planetary part is called a first-stage planetary part. Three first-stage planetary gears P1 mesh with the first-stage sun gear S1 and the first-stage internal gear (ring gear) R1. Is called a second stage planetary portion, and five second stage planetary gears P2 are meshed between the second stage sun gear S2 and the second stage internal gear (ring gear) R2. There is a correlation between the reduction ratio i of the planetary gears and the number of planetary gears. As shown in FIG. 6, the reduction ratio i is determined by the pitch circle diameter dR of the internal gear (ring gear) R and the sun gear S. In general, when the pitch circle diameter dR is larger than the pitch circle diameter dS, the reduction ratio i increases, but conversely, the sun gear S and the internal gear R The number of the planetary gears P that can be stored between them decreases. On the other hand, as the number of the planetary gears increases, the share of the power transmission force to each planetary gear decreases, and the diameter dR of the internal gear (ring gear) R is relatively smaller than the diameter dS of the sun gear S. The reduction gear 2 can be made compact.
【0014】本発明の場合には、従来のベベル部を有す
る減速機(図10に示すもの)に比べてベベル部のない
分高さを低くできるから、上下2段の遊星減速機とする
ことができる。そして、上述の従来型ベベル型遊星減速
機(例えば、ベベル減速比iB=4、遊星部減速比iP=1
0)と同様に、減速比40の竪型二段遊星減速機を設け
るには、1段(下段)減速比i=8.9(遊星個数3
個)、2段(上段)減速比i=4.5(遊星個数5個)
とし、減速機全体の大きさ(直径)は、5個の遊星歯車
を保有する本発明の場合の二段遊星減速機が従来型に比
べて小さくなり、コンパクト化される。In the case of the present invention, since the height without the bevel portion can be reduced as compared with the conventional speed reducer having a bevel portion (shown in FIG. 10), a two-stage planetary speed reducer is used. Can be. Then, the above-described conventional bevel type planetary reduction gear (for example, bevel reduction ratio iB = 4, planetary reduction ratio iP = 1)
Similarly to the case of 0), in order to provide a vertical two-stage planetary reduction gear having a reduction ratio of 40, a one-stage (lower) reduction ratio i = 8.9 (the number of planets is 3)
), 2nd (upper) reduction ratio i = 4.5 (5 planets)
The size (diameter) of the entire speed reducer is smaller than that of the conventional two-stage planetary speed reducer having five planetary gears in the case of the present invention, and the size is reduced.
【0015】このように、本発明における竪型粉砕機1
においては、従来構造のように減速機2に鉛直荷重を与
えることなく、熱変形から保護された静圧軸受によって
減速機2とは別途に回転テーブル3Aの自重や油圧シリ
ンダ9によって付与される粉砕力などの鉛直荷重を支持
する機構としている。したがって、減速機2は回転駆動
のための回転トルクの伝達だけの機能があればよく、そ
れだけ小型化できるとともに、粉砕仕事中の負荷変動に
伴う振動現象の影響を受けることが少なく、振動トラブ
ルによる損傷が軽減され長寿命が達成される。また、減
速機は従来タイプに比べて小径化されるので、減速機の
分解作業に際してあらかじめ粉砕機部分(ケーシング1
5や回転テーブル3Aなど)を吊り上げ除去した後に、
上方へ吊り上げ移動が可能となり作業時間の短縮と作業
効率の向上が図られる。また、ピット100を形成し電
動機2Bを竪型電動機として減速機2の直下に配設して
直結としたため、減速機2はベベル部のない竪型二段遊
星減速機を採用できるので、減速機2が小型コンパクト
化し、それに応じて竪型粉砕機足回りもコンパクト化
し、省スペースを実現できる。また、従来地上部分にあ
った電動機2Bがピット100内に収納されるから省ス
ペースは一層達成される。As described above, the vertical pulverizer 1 according to the present invention is used.
In the conventional method, the vertical load is not applied to the speed reducer 2 as in the conventional structure, and the static pressure bearing protected from thermal deformation separates from the speed reducer 2 by the weight of the rotary table 3A and the pulverization applied by the hydraulic cylinder 9. The mechanism supports vertical loads such as force. Therefore, the speed reducer 2 only needs to have a function of transmitting the rotational torque for the rotary drive, and can be reduced in size accordingly, and is less affected by the vibration phenomenon caused by the load fluctuation during the pulverization work. Damage is reduced and long life is achieved. In addition, since the reduction gear has a smaller diameter than that of the conventional type, a crusher portion (casing 1
5 and rotating table 3A)
Lifting and moving can be performed upward, thereby shortening the working time and improving the working efficiency. Further, since the pit 100 is formed and the electric motor 2B is disposed as a vertical electric motor immediately below the speed reducer 2 and directly connected to the speed reducer 2, the speed reducer 2 can be a vertical two-stage planetary speed reducer without a bevel portion. 2 is compact and compact, and accordingly the underbody of the vertical pulverizer is also compacted, and space can be saved. In addition, since the electric motor 2B conventionally located on the ground is stored in the pit 100, space saving is further achieved.
【0016】[0016]
【発明の効果】以上説明したように、本発明によれば減
速機には鉛直荷重が負荷されず減速機の小型軽量化が実
現され、それに応じて竪型粉砕機の足回りも省スペース
化し、設備費が低減されるとともに、粉砕中の異常振動
に伴う減速機トラブルが回避され、メンテナンス性が向
上する。また、回転テーブルの熱変形が小さく、熱変形
による悪影響が静圧軸受に及ばないように配慮されてい
るので、静圧軸受が損傷されることなく長寿命を達成す
ることができる。As described above, according to the present invention, a vertical load is not applied to the speed reducer, and the size and weight of the speed reducer can be reduced. In addition, the equipment cost is reduced, and the trouble of the reduction gear caused by the abnormal vibration during the pulverization is avoided, and the maintainability is improved. In addition, since the thermal deformation of the rotary table is small so that the adverse effects of the thermal deformation do not affect the hydrostatic bearing, a long life can be achieved without damaging the hydrostatic bearing.
【図1】本発明の実施例に係る竪型粉砕機の全体縦断面
図である。FIG. 1 is an overall vertical sectional view of a vertical crusher according to an embodiment of the present invention.
【図2】図1のA−A視の断面平面図である。FIG. 2 is a sectional plan view taken along line AA of FIG.
【図3】本発明の実施例に係る竪型粉砕機の要部縦断面
図である。FIG. 3 is a vertical sectional view of a main part of a vertical crusher according to an embodiment of the present invention.
【図4】本発明の実施例に係る静圧軸受部の要部拡大縦
断面図である。FIG. 4 is an enlarged vertical sectional view of a main part of a hydrostatic bearing according to an embodiment of the present invention.
【図5】本発明の実施例に係る減速機(竪型二段遊星減
速機)の縦断面図である。FIG. 5 is a longitudinal sectional view of a speed reducer (vertical two-stage planetary speed reducer) according to an embodiment of the present invention.
【図6】本発明の実施例に係る遊星減速機の説明図であ
る。FIG. 6 is an explanatory diagram of a planetary reduction gear according to an embodiment of the present invention.
【図7】本発明の実施例に係る回転テーブルの熱歪解析
状態図である。FIG. 7 is a thermal distortion analysis state diagram of the turntable according to the embodiment of the present invention.
【図8】本発明の実施例に係る回転テーブルの熱歪解析
状態図である。FIG. 8 is a thermal distortion analysis state diagram of the turntable according to the embodiment of the present invention.
【図9】本発明の実施例に係る回転テーブルの熱歪解析
状態図である。FIG. 9 is a thermal distortion analysis state diagram of the turntable according to the embodiment of the present invention.
【図10】従来の竪型粉砕機の全体縦断面図である。FIG. 10 is an overall vertical sectional view of a conventional vertical crusher.
1 竪型粉砕機 2 減速機(遊星減速機) 2A 寸動電動機 2B 電動機 2a 出力軸 3A 回転テーブル 3B フランジシュー 3C 回転筒 3S ダムリング 3X 平板部 3Y 外周円筒部 3Z 内周円筒部 4 粉砕ローラ 5 アーム 6 軸(回転軸) 7 アーム 7A アーム 7B アーム 9 油圧シリンダ 14 環状空間通路 15 ケーシング 16 排出口 17 原料投入シュート 17A 分岐管 17B 堰板 18 スクレーパ 19 排出シュート 30 柱脚 30A ステー 30B 固定リング 30P 支持板 30Q 支持柱 30a 静圧軸受(スラストパッド) 30b 支持環 31 ベースメタル 32 軸受メタル 33 潤滑給油口 34 給油路 35 球状ピボット 40 スタンド 50 スリット 100 ピット P 遊星歯車 P1 第1段遊星歯車 P2 第2段遊星歯車 R 内歯歯車(リングギア) R1 第1段内歯歯車(リングギア) R2 第2段内歯歯車(リングギア) S 太陽歯車 S1 第1段太陽歯車 S2 第2段太陽歯車 dR 内歯歯車のピッチ円直径 dS 太陽歯車のピッチ円直径 i 減速比 iB ベベル減速比 iP 遊星部減速比 DESCRIPTION OF SYMBOLS 1 Vertical grinder 2 Reduction gear (planetary reduction gear) 2A Inching motor 2B Electric motor 2a Output shaft 3A Rotary table 3B Flange shoe 3C Rotating cylinder 3S Dam ring 3X Flat plate part 3Y Outer cylinder part 3Z Inner cylinder part 4 Crush roller 5 Arm 6 axis (rotating axis) 7 Arm 7A Arm 7B Arm 9 Hydraulic cylinder 14 Annular space passage 15 Casing 16 Discharge port 17 Material input chute 17A Branch pipe 17B Weir plate 18 Scraper 19 Discharge chute 30 Column base 30A Stay 30B Fixing ring 30P Support Plate 30Q Support column 30a Hydrostatic bearing (thrust pad) 30b Support ring 31 Base metal 32 Bearing metal 33 Lubrication oil supply port 34 Oil supply path 35 Spherical pivot 40 Stand 50 Slit 100 Pit P Planetary gear P1 First stage planetary gear P2 Second stage Planetary gear Internal gear (ring gear) R1 First stage internal gear (ring gear) R2 Second stage internal gear (ring gear) S Sun gear S1 First stage sun gear S2 Second stage sun gear dR Pitch of internal gear Circle diameter dS Pitch circle diameter of sun gear i Reduction ratio iB Bevel reduction ratio iP Planetary reduction ratio
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭52−144858(JP,A) 実開 昭50−140059(JP,U) 実開 平5−67334(JP,U) 実開 昭63−20952(JP,U) (58)調査した分野(Int.Cl.7,DB名) B02C 15/00 - 15/16 ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-52-144858 (JP, A) JP-A 50-140059 (JP, U) JP-A 5-67334 (JP, U) JP-A 63-144 20952 (JP, U) (58) Fields investigated (Int. Cl. 7 , DB name) B02C 15/00-15/16
Claims (3)
転自在な粉砕ローラを配設し、回転テーブル上に供給さ
れた原料を粉砕ローラに所定の圧力を与えて回転テーブ
ル上面と粉砕ローラ周面との間で粉砕する竪型粉砕機に
おいて、該回転テーブルに回転力を付与する減速機を該
回転テーブル直下の中央部に配設するとともに、該回転
テーブルに負荷される自重ならびに粉砕力などの鉛直荷
重を支承する静圧軸受を該回転テーブル外周部の粉砕ロ
ーラ押圧領域の直下に配設し、該静圧軸受を支承する柱
脚を該減速機とは別体に設け、該静圧軸受は前記柱脚の
上面との間に球状ピボットを介して押圧されるセンタピ
ボットタイプの軸受とするとともに、該静圧軸受の側面
には水平方向の移動を抑止する側面押えを配設し、か
つ、該回転テーブルは粉砕ローラが載置される平板部と
該平板部の外周下方へ延在し前記静圧軸受に下端が支承
されある程度の高さを保有し肉厚を薄くした外周円筒部
と該平板部の中心部下方へ延在し前記減速機の出力軸と
下端が係合される内周円筒部を有する形状とし、該回転
テーブルに負荷される鉛直荷重が該外周円筒部をほぼ垂
直に伝わって該静圧軸受で支承される構成にし、該内周
円筒部を、該内周円筒部の下端に一体的に取付けた回転
筒、及び、該回転筒の外周囲に内周面が摺動可能とされ
て嵌装された支持環を介して、支持するためのステーを
該柱脚との間に円周複数本設けた竪型粉砕機。1. A plurality of rotatable crushing rollers are disposed on an upper surface of an outer peripheral portion of a rotary table, and a predetermined pressure is applied to the crushing rollers for the raw material supplied on the rotary table to apply a predetermined pressure to the rotating table. In a vertical pulverizer for pulverizing between a surface and a surface, a reducer for applying a rotational force to the rotary table is disposed at a central portion immediately below the rotary table, and the own weight and the pulverizing force applied to the rotary table A static pressure bearing for supporting the vertical load of the rotary table is disposed directly below the grinding roller pressing area on the outer periphery of the rotary table, and a column base for supporting the static pressure bearing is provided separately from the speed reducer. The bearing is a center pivot type bearing pressed through a spherical pivot between the bearing and the upper surface of the column base, and a side retainer for suppressing horizontal movement is disposed on a side surface of the hydrostatic bearing, And the rotary table is A flat plate portion on which a crushing roller is mounted, an outer peripheral cylindrical portion extending downwardly on the outer periphery of the flat plate portion and having a lower end supported by the hydrostatic bearing and having a certain height and a reduced thickness, and a center of the flat plate portion. A vertical cylindrical portion extending downwardly and engaging the output shaft of the speed reducer with a lower end thereof. The vertical load applied to the rotary table is transmitted substantially vertically through the outer cylindrical portion, and the static Pressure bearing, and the inner circumference
Rotation in which the cylindrical part is integrally attached to the lower end of the inner peripheral cylindrical part
The inner peripheral surface is slidable around the outer periphery of the cylinder and the rotating cylinder.
The stay for supporting via the support ring fitted
A vertical crusher provided with a plurality of circumferences between the column base .
項1記載の竪型粉砕機。2. The vertical pulverizer according to claim 1, wherein the speed reducer is a vertical two-stage planetary speed reducer.
機を回転駆動する竪型電動機を該ピット内に配設した請
求項1または請求項2記載の竪型粉砕機。3. The vertical pulverizer according to claim 1, wherein a pit is formed immediately below the speed reducer, and a vertical electric motor for rotating and driving the speed reducer is disposed in the pit.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP06228215A JP3105405B2 (en) | 1994-09-22 | 1994-09-22 | Vertical crusher |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP06228215A JP3105405B2 (en) | 1994-09-22 | 1994-09-22 | Vertical crusher |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH0889829A JPH0889829A (en) | 1996-04-09 |
JP3105405B2 true JP3105405B2 (en) | 2000-10-30 |
Family
ID=16872992
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP06228215A Expired - Fee Related JP3105405B2 (en) | 1994-09-22 | 1994-09-22 | Vertical crusher |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP3105405B2 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2777814B1 (en) * | 2011-11-11 | 2019-05-01 | Kawasaki Jukogyo Kabushiki Kaisha | Vertical roller mill |
JP5809708B2 (en) * | 2011-11-11 | 2015-11-11 | 川崎重工業株式会社 | Vertical roller mill |
CN103191803B (en) * | 2013-04-19 | 2015-03-04 | 二重集团(德阳)重型装备股份有限公司 | Vertical roller mill |
CN106246875B (en) * | 2016-08-19 | 2018-10-16 | 重庆齿轮箱有限责任公司 | A kind of roller mill speed reducer |
CN106382358B (en) * | 2016-08-19 | 2018-10-16 | 重庆齿轮箱有限责任公司 | A kind of roller mill speed reducer |
-
1994
- 1994-09-22 JP JP06228215A patent/JP3105405B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
JPH0889829A (en) | 1996-04-09 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US4339086A (en) | Grinding pan bearing arrangement and drive of a roller mill | |
US7926754B2 (en) | Safety systems for roller mills | |
JP5683450B2 (en) | Roller mill | |
US5616098A (en) | Reduction mechanism for mill and mill having the same | |
JP3105405B2 (en) | Vertical crusher | |
CN101173318A (en) | Blast furnace distributor | |
JP2956882B2 (en) | Vertical crusher | |
CN103191803B (en) | Vertical roller mill | |
KR0167396B1 (en) | A vertical type roller mill | |
CN103521310A (en) | Ball mill unit for preparation of burning coal-water slurry | |
JP2956878B2 (en) | Vertical crusher | |
JP3011313B2 (en) | Vertical crusher | |
JPS61157364A (en) | Shearing crusher | |
WO2009000575A1 (en) | Rolling bearing | |
US20130008989A1 (en) | Roller mill | |
JP2956879B2 (en) | Disassembly inspection and maintenance method of reduction gear for vertical crusher | |
JPH0824691A (en) | Vertical crusher | |
JPH0838922A (en) | Vertical pulverizer | |
JPH0880446A (en) | Vertical pulverizer | |
AU635674B2 (en) | A method of operating a mill and a mill operated in accordance with the method | |
CN219408175U (en) | Tilting prevention sliding device of turnover machine | |
CN102896022A (en) | Automatic pressurizing device for grinding roller of flour mill | |
CN211540863U (en) | Grinding machine maintenance cover | |
JP2001140877A (en) | Preloaded tapered roller bearing and vertical rotary machine using it | |
CN117427732A (en) | Vertical roller mill driven by grinding roller and grinding method thereof |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080901 Year of fee payment: 8 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090901 Year of fee payment: 9 |
|
LAPS | Cancellation because of no payment of annual fees |